Mining machine



Aug. 20, 1940.

J. F. JOY ETAL MINING MACHINE Filed July 15, 1956 @y di@ 14 Sheets-Sheet l Aa WM J. F. JOY El' AL MINING MACHINE Aug. 2o, 1940.

Filed July l5, 1936 14 Sheets-Sheet 2 ,RA mw ma aww xv ww Nw mw L 2mg Aug 20, 1940- J. F. JOY ET A1. 2,211,781

MINING MACHINE Filed July 15, 1956 14 sheets-sheet 5 Aug. 20, 1940. .1. F. JoY Er A1. 2,211,781

MINING MACHINE Filed July 15, 1936 14 Sheets-Sheet 4 Eff? wf /6/ my ug. 20, 1940. J. F. JOY ET A1.

MINING' MACHINE Filed July 15, 1936 v14 Sheets-Sheet 5 ug. 20, 1940. L F, JOY ET AL 2,211,781

MINING MACHINE Filed July 15, 1936 14 Sheets-Sheet 6 J. F. JOY El' AL MINING MACHINE Aug. 20, 1940.

Filed July l5, 1936 14 Shets-Sheet '7 QM I W I www w w www Qww uw www WM im m www b d HREN J@ wm A ,w l ul .u .c MW n o v w y w j ,o w w .www m, www Nw N l|l|||l N|\|||,1|1|I|.,f|| IWWN/QNN.. .ALI

l l u IL Aug. 20, 1940. J. F, JOY Er AL MINING MACHINE Filed July 15, 1936 14 Sheets-Sheet 8 Aug. 20, 1940.

J. F. JOY El AL MINING MACHINE Filed July 15, 193s lll Illl

14 Sheets-Sheet 9 y 74M; A Mm,

J. F. JOY E T AL MINING MACHINE Filed July l5, 1936 14 Sheets-Sheet 10 EMI@ mw@ w I Aug. 20, 1940. .1. F. JOY Er A1.

MINING MACHINE Aw; -4' MM magy Aug. 20, 1940. J. F. JOY r A1.

MINING MACHINE Filed July 15, 1936 14 Sheets-Sheel l2 I r a 2 0 qm J. w .y W p, WMu -w w v w. 7 www www www www. www m www www www www n A n d [l I I u www w ww\ 6 ww au www .www w "Vor www Awww www www w www www\ www www www w ww www@ www www www w www www wwwww\ ww\ www www www www o www. w\m

www www www www@ ww J, F. JOY ET AL MINING MACHINE Aug. 20, 1940.

Filedf July 15, 193s 14 Sheets-Sheet 13 www uw Awww. W RMV@ www MU %N% uw. www W A111120, 1940. J. F. JOY ET A1 2,211,781 MINING MACHINE Filed July 15, 1936 14 Sheets-Sheet 14 11min!!! Il f! Il H] .ma

Patented Aug. 20, 1940 UNITED STATES MINING MACHINE Application July 15, 1936, Serial No. 90,744

15 Claims.

This invention relates to'mining machines and more particularly, but not exclusively, to improvements in coal mining machines of the iiexibly fed, floor cutter type.

An object of this invention is to provide an improved coal mining machine having improved features of construction whereby the kerf cutting means may be operated and controlled in an improved and more effective manner. Another object is to provide an improved coal mining machine of the flexibly fed, floor cutter type having improved means for feeding and guiding the machine dung the cutting operation. A further object is to provide an improved coal mining machine of the combined room and pillar and longwall type whereby the machine may operate in accordance with either the room and pillar or longwall system of mining. Still another object is to provide an improved coal mining machine of the flexibly fed, floor cutter type wherein relatively rotatable feed operating and controlling members respectively adapted to cooperate with flexible feeding and controlling elements, are employed for feeding and guiding the machine, and having improved means for driving and controlling the feed operating and controlling members. A still further object is to provide an improved mining machine transmission mechanism which is extremely compact, and whereby the feed operating and controlling members may be drivenin an improved manner. These and other objects and advantages of the invention will, however, hereinafter more fully appear.

In the accompanying drawings, there are shown for purposes of illustration several forms which the invention may assume in practice.

In these drawings- Fig. 1 is a plan View of one illustrative embodiment of the improved mining machine, a portion of the casing being broken away to illustrate details of construction;

Fig. 2 is a side elevational View of the machine shown in Fig. 1;

Fig. 3 is an enlarged fragmentary plan View of the machine shownin Fig. 1, with the top cover plate partially broken away to show details of the interior construction;

4 is an enlarged view in longitudinal vertical section taken substantially on line lil-4 of Fig. 1;

Fig. 5 is a detail sectional View taken substantially on line 5-5 of Fig. 3;

Fig. 6 is a detail sectional view taken substantially on line 6-6 of Fig. 3;

(Cl. 'i4-389) Fig. '7 is an enlarged cross sectional view taken substantially on line l-l of Figs. 1 and 3;

Fig. 8 is an enlarged vertical sectional view taken substantially on line 8 8 of Fig. 3;

Fig. 9 is an enlarged end elevational view of the machine shown in Figs. l and 2, a portion of the casing being broken away to show details of construction;

Fig. 10 is a diagrammatic view showing the hydraulic fluid system and the associated control means;

Figs. 11 and 12 are views similar to Figs. 1 and 2, respectively, showing a modified form of construction;

Fig. 13 is an enlarged View in longitudinal vertical section taken substantially on line iiii3 0f Fig. 11;

Fig. 14 is an enlarged View in longitudinal vertical section taken substantially on line ffii-ill of Fig. 11;

Fig. 15 is an end elevational View of the machine shown in Figs. 11 and 12;

Fig. 16 is a cross sectional View taken substantially on line i-l of Figs. 11 and 17;

Fig. 17 is an enlarged fragmentary plan view of the machine shown in Fig. 11, a portion of the casing broken away to show details .of the interior construction;

Fig. 18 is a detail Vertical sectional View taken on line Iii-i8 of Fig. 11, showing the kerf cutter lock;

Fig. 19 is a cross sectional view taken substantially on line l9l9 of Fig. 11;

Fig. 20 is a diagrammatic view showing the hydraulic uid system and the associated control means;

Figs. 21 and 22 are views similar to Figs. 1 and 2, respectively, showing a further modified form of construction;

Fig. 23 is an enlarged view in longitudinal vertical section taken substantially on line 23-23 of Fig. 21;

Fig. 24 is an end elevational view of the machine shown in Figs. 21 and 22;

Fig. 25 is a detail vertical sectional view taken substantially on line 25-25 of Fig. 2l;

Fig. 26 is an enlarged cross sectional View taken substantially on line i-Z of Fig. 21;

Fig. 27 is a detail view in longitudinal vertical section taken substantially on line 'l-2l of Fig. 21.

In the several embodiments of the invention, there is shown a coal mining machine of the combined room and pillar and longwall, flexibly fed, floor cutter type, although it will be evident that various features of the invention may be incorporated in mining machines of various other types.

In the illustrative embodiment of the invention disclosed in Figs. 1 to 10, inclusive, the mining machine generally comprises a casing I' of low, compact, generally rectangular shape having a smooth bottom surface 2 and adapted to rest upon and slide in any direction over the mine floor. The machine casing I comprises a feed and cutter frame section 3, a motor frame section 4 and a control and guide frame section 5, and the casing sections are rigidly united in any suitable manner. Arranged within a transverse horizontal chamber S, extending across the lower portion of the casing section 3 at one end of the motor casing section, are relatively rotatable feed operating and controlling members, herein in the form of cable winding drums l' and 8 having respectively wound thereon feeding and controlling cables 9 and li?, while projecting horizontally from the machine casing l is an elongated, horizontal plane kerf cutter Il.

Now referring to the improved driving means for the kerf cutter, it will be noted that arranged within the motor casing l!- is a motorjherein preferably of the reversible electric type, having its power shaft I2 horizontally disposed and extending longitudinally of the machine, with its axis of rotation lying in the central longitudinal vertical plane of the machine. Formed integral with the motor power shaft, at one end of the motor, is a spur motor pinion I3 meshing with a spur gear lli (see Fig. 4) keyed to a horizontal longitudinally extending shaft i5. The shaft I5 is arranged parallel with and in horizontal planes above the motor power shaft and suitably journaled within the casing section 3. Keyed to and driven by the shaft l5 is a bevel gear IB meshing with a horizontal bevel gear I'I having its hub journaled on bearing sleeves supported by a clutch sleeve I3 keyed to a vertical shaft I'9. As illustrated, the casing section 3 is provided, at one end thereof, with a projecting bearing frame and gear housing 25) of partially cylindrical shape providing a housing for the bevel gears IG, Il, and the vertical shaft I9 is journaled on this frame portion Eil. The upper portion of the frame portion is provided with an upstanding circular bearing support 2 I, while depending from the lower portion of the frame portion is a circular bearing support 22, and the shaft i9 is journaled in ball bearings arranged within these bearing supports in the manner shown in Fig. 4. Formed on the hub of the bevel gear Il are clutch teeth 23 connectible, by a sliding clutch member 241, to clutch teeth 25 formed on the clutch sleeve I8. 'The sliding clutch member 24 is operated by a shipper yoke 2G mounted on a longitudinal shaft 2l journaled in the casing section 3 and having an arm 28 connected by a link 29 to a crank 3Q fixed to an operating rod 3I As shown in Fig. l, this operating rod extends longitudinally of the machine casing along one side thereof and has fixed thereto, at its opposite end, an operating lever 32 so that the clutch may be controlled from the operators station at the end of the machine remote from the kerf cutter. Keyed to the vertical shaft I9 and driven thereby is a chain sprocket 33 engaging and driving an endless cutter chain 34 mounted for circulation about the margin of a cutter bar 35 of the kerf cutter. It will thus be seen that when the sliding clutch 2li is connected, the cutter chain 34 may be driven from the motor power shaft I2 through the spur gearing I3, Ill, shaft I5, bevel gearing I6, I7 and the vertical shaft i9; and, when the clutch is disconnected, the cutter chain may remain idle during running of the motor.

The pivotal mounting for the cutter bar 35 for supporting the latter for swinging movement about a pivotal axis coincident with the axis of the cutter drive .shaft I9 comprises a hanger frame 3'5 having a cylindrical bearing portion 31 journaled on a bearing sleeve supported by the cylindrical hearing support 22. Formed integral with the hanger frame is an upstanding frame portion 58 having secured thereto a bearing frame 35 overlying the upper portion of the frame portion of the casing section 3 and journaled on bearing sleeves supported by the circular bearing support 2l. It will thus be seen that the cutter bar has a pair of spaced bearing supports on the machine casing, resulting in an extremely stable pivotal mounting for the cutter bar.

f the improved flexible feeding means, and more part .,arly to the driving means therefor, it will be noted that keyed to and driven. by the lon tudinal cutter drive shaft i5 is a worm meshing, at its opposite sides, with horizontal worm wheels GI and 2, herein arranged on parallel vertical lying in a vertical plane extending transversely of the machine and spaced equidistantly from a longitudinal vertical plane including the axis of rotation of the shaft I5. c .amber 6, within which the cable winding drums are arranged, lies in a transverse zone between the motor and the korf cutter, and these drums are arranged on parallel vertical axes alined with the axes of the worm wheels fil and Z272, respectively. Rotatable with and driven by the worm wheels /II and respectively, are spur gears 43 and Gl! meshing with spur gears l5 and (la, herein erranged on vertical axes spaced equi-distantly from a longitudinal vertical plane including the axis of rotation of the shaft i5 and parallel with the worm Wheel axes. The hubs i? of the spur gears [l5 and d5 are connectible by conventional multiple disc clutches M and G9, respectively, to alined vertical shafts 5C' and 5i. Rotatable with and driven by these vertical shafts are spur gears 52 and 53 meshing with spur gears 5? and 55, herein arranged coaxially '-.vith the worm wheels 4I and 42, respectively, in hcrizontal planes below the latter, as clearly shown in Fig. '7. The worm wheels II and Il?! are connectible by conventional multiple disc clutches and 57, respectively, to the upstanding hubs 5I? of the spur gears 56 and The hubs of the worm wheels and the spur gears are ,iournaled on ball bearings supported by vertical shafts 59 and 6D arranged coaXially with the worm. wheels respectively, these shafts being threadedly secured at GI, at their upper ends within the top of the casing section and fixed at their lower ends at S2. within cylindrical bearingr supports formed int al withI the bottomof the casing section.. Formed on the bottoms of the spur gears 50.., 55 clutch teeth Si! connectible by sliding clutch members G5 to clutch teeth 6G formed on the cable Winding drums 'i and S, respectively, so that when these clutches are connected the drums may be driven by either: the worm wheels or the spur gears. The worm wheels 4I and 42 constitute the high speed terminal driving elements for the drums, while the spur gears 54 and 55 constitute the low speed terminal driving elements; and, when the friction clutches 68 and 49 are applied and the clutches 56 and 51 released, the drums may be driven in cable winding direction at a relatively low speed appropriate for cutting; and, when the clutches 48 and 49 are released and the clutches 58 and 51 applied, the drums may be driven in cable winding direction through the Worm wheels at a relatively high Inachine haulage speed. As shown in Fig. 7, each of the cable winding drums has, at its upper side, a sleeve-like hubl 'l journaled in roller bearings 68 supported within a bearing -hub 69 formed integral with the casing section 3, while the lower sides of the drums are journaled on roller bearings 'IIJ supported by the bearing support 63. Each drum is supported by a thrust ring 'li on the bearing hub S3 (see Fig. 7), and a packing 12 provides a lubricant and dust seal for the lower drum bearing l, while a similar packing 13 provides a lubricant and dust seal for the upper drum bearing 68.

In this instance, a retarding friction or brake is provided for each cable winding drum so that rotation of the drums in unwinding direction may be frictonally resisted when the drums are disconnected from their driving means; and these retarding frictions comprise, as shown in Fig. 8, spur gears 'l5 Sand 'i6 meshing with the spur gears 54 and 55 respectively, and rotated by the latter. These spur gears 'I5 and 16 are formed integral with vertical shaftsy 'H and 'I8 journaled in ball 4bearings suitably journaled in the casing section 3; and keyed to the upper portions of each of these shafts is a series of frictional braking discs 'i9 interleaved with a series of frictional braking discs Si) keyed to a cylindrical bearing support 8| within Which the upper ball bearings for the shafts are supported. Circular plates 82 having projections 83 engageable with the upper non-rotatable discs are provided for pressing the interleaved discs together, thereby to frictionally retard rotation of the spur gears meshing with the spur gears 54 and 55. The means for operating the clutch applying plate 82 will be presently described. The locking means for locking the kerf cutter in its different adjusted positions about its pivot comprises, as shown most clearly in Fig. 8, a vertical cylinder 85 supported at 86 within a bore in the kcasing section 3' and containing a reciprocable piston B'l. Secured to the piston 8l is a locking pin 33 adapted to project in one of a series of locking apertures 39 formed in the hanger frame 35 for the cutter bar 35. Threaded at 90 on the upper end of the cylinder 85 is a cap 9| having a chamber within which is arranged a coil spring 92 acting on the upper surface of the piston 81 for urging the locking pin 88 towards its locking position. A packing 93 embraces the locking pin 88 :for providing a seal between the cylinder bore at the lower side of the piston and the movable locking pin. Hydraulic pressure may be supplied to the cylinder bore at the lower side or the piston 8l to move the piston upwardly against the tension of the coil spring 92, thereby to release the locking pin from the locking aperture in the cutter bar hanger frame in a manner to be later described.

Now referring to the improved hydraulic control means for the various friction clutches, the drum release clutches, the retarding frictions and the kerf cutter lock, it will be noted that supported on the casing section 5 is a valve box 95 having horizontal bores containing rotary control valves 95, Sl, 98, 99, and lill. Formed within the casing section is a lubricant reservoir |02 having mounted therein a hydraulic pump |93, preferably of the interrneshing gear type and driven from the rear end of the motor power shaft l2; the pump having its discharge side connected through a conduit it@ to the supply passage I of the valve box. The discharge passage |66 of the valve box is connected by a discharge conduit lill back to reservoir m2.. Referring mlore particularly to the operating means for the disc clutches 5E and 5l, it will be noted that arranged Within the upper portion of the casing section 3 are Vertical bores HB3 each containing a reciprocable plunger |69, these plungers each engaging the upper race iii] of a ball thrust bearing i l i. The lower bearing races M2 engage vertical plungers H3 extending ythrough openings in the worm wheels and, in turn., engaging, at their lower ends, pressure applying plates Hfi for the discs .of the clutches. Interposed between the worm wheel hubs and the lower thrust bearing races M2 and encircling the plungers H3 are coiled springs H5 for normally urging the plungers M19 toward their uppermost clutch releasing position. The upper ends of the hores containing the plungers H39 are connected, through branched conduits HG, in turn connected through conduits lll and Elli, to the bores for the valves Q6 and i; and, when these valves are in the position shown in Fig. .1.0, hydraulic pressure may how, through the conduit |013, supply passage l G5, passages on the Valves 96 and mi?, the conduits lll and M3 to the branched conduits M6, and thence to the bores at the upper sides oi the plungers m9; and as a result the latter are moved downwardly by the hydraulic pressure acting thereon, smoothly to apply a loading pressure to the discs of the friction clutches. The controlling means for the friction clutches 48 and 69 for the low speed terminal gears comprises, as shown in Fig. 8, annular bores H9 each containing an annular plunger i2@ engageable, through a ball thrust bearing |2l, with vertical plungers |22 guided in openings in the spur gear and secured to a pressure applying ring |23 engaging the upper disc of the clutch. The bores l i9 at the upper sides of the plungers |26 are connected, through conduits E24 and 525 to. the bores for the valves 9 and Hill, so that, when the valves are in the position opposite from that shown in Fig. i0, hydraulic pressure may flow from the pump w3, through the conduit EM, supply passage m5, passage on the valves 56 and Miti, and conduits i2@ and 25 to act on the upper surfaces of the plungers smoothly to load the discs of the clutches. It will thus be seen that, when the fast speed clutches are applied, the slow speed clutches are always released, and vice versa. The control means for the retarding frictions comprises bores |26 containing plungers |2lI engaging the upper surfaces of the pressure applying plates B2. The bores at the upper sides of the plungers 27 are connected, through conduits i252 and E29, to the bore of the valve 9d, so that, when the valve is in the position shown in 10, hydraulic pressure may ow through the conduit Mld, supply passage |05, a passage on the valve 93 and conduit |29, to move the plunger |274' downwardly to apply the retarding'friction for the spur gear l', while the retarding friction for the spur gear 15 is connected to exhaust through conduit 29, a passage on the valve 98, discharge passage H15, and discharge conduit l'l. When the position of the valve S8 is reversed, the retarding friction for the spur gear 'F6 is released, While the retarding friction for the spur gear 'i5 is applied. The operating means for the drum release clutches 66 each comprise a cylinder E3B on which the clutch member G6 is mounted and containing a plunger' |3|. Secured to the plunger |3| are operating rods |32 engaging the upper race |33 of a ball thrust bearing i3d, in turn engaging the lower bearing race i215 integral with the clutch member G53. The upper end of the bore of the cylinder |35 is packed by a packing member |36. Axial passages I3? formed in the shafts 59 and 65 respectively communicate, through radial passages |38, with the bores of the cylinders |39 at the upper sides of the plunger-s 3i, so that, when hydraulic pressure is applied to the cylinder bores, the clutch mem-y bers 6G are moved downwardly to release the clutch elements on the drums from the clutch elements on the gears 54 and 55 respectively. When the pressure is released from the cylinder bores at the upper sides of the plungers i3 l, coil springs |39, encircling the clutch members 5a, move the latter upwardly into their clutched position. The passages |37 in the shafts are connected, through conduits Mil, |45, to the bores for the valves Si and 99, so that, when the valves in the position shown in Fig. 10, hydraulic pre:- sure may flow from the conduit mi2, through supply passage H35, through passages on the valves 97 and 9 and through the conduits Mil, ill?, to move the plunger-s |S| downwardly to release the drum clutches 56. When the valves are turned into their position opposite from that shown in Fig. i0, the conduits MQ and tdi are connected to the discharge passage i so that the pressure acting on the plungers 35 is released and the drum clutches connected by the coil springs |38. The bar locking cylinder at the lower side of the plunger 87 is connected, through a conduit Effi-2, to the bore for the valve mi, so that, when the Valve is in the position shown in Fig. 10, hydraulic pressure may dow from the conduit |04, through discharge pas sage |55, a passage on the valve 59| and conduit |62, to the lower side of the plunger 3l' to move the locking pin 88 into its released position. Vthen the position of the valve il?! is reversed, the conduit M2 is connected to the discharge passage |96 so that the pressure below the plunger 8'? is released and the locking pin i3@ moved into its locking position by the coil spring By closing the valve, the locking pin may be maintained in its released position. It will be noted that the conduit |42 has a flared end (see Fig. 6) engaged by the tapered end of a plug Uil held in position on the frame by a set screw |652', thereby to provide a fluid-tight point. This structure enables the removal of the top cover of the casing without disturbing the conduit As shown in Fig. 9, arranged adjacent the control valves in the valve box is a by-pass control valve U53 having a manual operating plunger EL34 so that the operator may readily control the pressure in the hydraulic system. It is accordingly evident that the fast and slow speed friction clutches, the retarding frictions, the drum release clutches and the bar lock are all hydraulically controlled, thereby facilitating the operation thereof, it being only necessary to rotate the control valves into the proper positions; and, due to the fact that the control Valve levers are arranged in the rear end of the machine, it is possible to effect the control of the various devices of the machine at the operators station within his easy reach.

As previously mentioned, the cable winding drums 'l and 8 are arranged within the transverse chamber 6 in a transverse zone between the motor and the kerf cutter; and the cables 9 and |0 wound on these drums are adapted to be extended from the machine in various manners to effect maneuvering and feeding or" the machine and to swing the kerf cutter about its pivot. Arranged on parallel vertical axes at the opposite sides of the casing section 3 are sets of horizontal guide rolls |45 and |46, these guide rolls being arranged at the opposite corners of the chamber 6, while journaled on the horizontal axes in coaxial relation, at the opposite sides of the casing section 5, are vertical guide rolls |47. Arranged at the rear of the guide rolls |47, are horizontal guide rolls M9 and |50, each mounted on a swingable bracket |5| pivoted on a vertical axis at |52. The brackets |5| are each engageable in their' different positions with suitable stop lugs |53 on the casing section 5. Formed on the hanger frame 3S for the cutter bar is an arcuate cable guiding groove |54; and integral with the hanger frame, near the ends of the groove |54, are hook-shaped portions |55 to which eye members |55, xed to the free ends of the cables, are connectible. Either of the cables may be extended from its winding drum about the guiding groove on the hanger frame into connection with a hook-shaped portion |55; and, when the bar lock 88 is released and the cable is wound in by its drum, the cutter bar may be swung about its pivot relative to the machine casing. One cable may be employed for eiecting cutter bar swing in one direction and the other cable to eiect cutter bar swing in the opposite direction. When the cutter bar is swung into the desired angular position with respect to the machine casing, it may be locked to the casing by the locking pin 88.

The general mode of operation of the improved mining machine is as follows: The cables may be extended in various directions from the machine about the guide rolls |45, |45, |41, |49 and |53. The cable i0 may be extended from the drum 8 rearwardly around the rear guide roll |45, around the vertical guide roll Ml' and then forwardly along the side of the machine and about the guiding groove |54 on the hanger frame into connection with one of the hook-like members |55, so that, when the cable is wound in,'the cutter bar may be swung about its pivot, and the cable 9 may be extended in a similar manner from the winding drum 'i'. Either of the cables may be extended from the winding drums around the forward guiding rolls |45, |46, laterally from the sides of the machine to a suitable anchor jack located at the rib, so that, when the cable is wound in, the machine may be fed laterally across the coal face. Either of the cables may be extended from the drums rearwardly around the rear guide rolls |45, |46, beneath the guide rolls IM' and around the guide rolls |49 and i5@ laterally from the rear end of the machine to a. suitable anchor jack located at the rib so that either cable may act as a guiding cable to control the angular position of the machine with respect to the coal face. The machine may be fed rapidly over the mine floor by either of the cables 9 and i5 under the control of the high speed friction clutches 56 and 51, and may be fed over the mine floor during the cutting operation at a relatively slow cutting speed under the control of the low speed clutches 48, 49. When the high and low speed clutches are released, the drums 'may rotate in unwinding direction under various degrees of frictional resistance regulated by the retarding frictions 19, 8|), The operator, by manipulating the control lever's of the various control valves, may regulate the supply of hydraulic pressure flowing to the control plungers for the various clutches, the retarding frictions and the cutter bar lock, so that the control, drum releasing and retarding frictions may be hydraulically applied and the cutter bar lock hydraulically released. The machine is of the combined room and pillar and longwall type, capable of operating in accordance with either the room and pillar or' longwall system of mining, the cutter bar being sumped into the coal either by bodily moving the machine endwise or swinging the cutter bar, and the machine fed bodily along the coal i'ace in the manner well understood by those skilled in the art. The machine is also reversible and may be operated to cut in either of opposite directions simply by reversing the motor, rearranging the cables on the drums and reversing the cutters of the cutter chain.

As previously mentioned, the flexible feeding and guiding means for the machine is similar to the form of the invention above described. Referring more particularly to the driving means for the feeding and guiding means, it will be noted that keyed to the end of the motor power shaft opposite from the bevel gear V12 is a spur pinion 209 meshing with a spur gear 2|@ keyed to a longitudinally extending shaft 2li. The shaft 2li is arranged with its axis parallel with and in horizontal planes above the motor power shaft axis, and is suitably journaled within the feed frame section ltd. Fixed to and driven by the shaft 2| is a worm 2|2 meshing, at its opposite sides, with horizontal worm wheels 2|@ and 2M, herein arranged on parallel vertical axes lying in a vertical plane extending transversely of the machine and spaced equidistantly from a longitudinal vertical plane including the axis of rotation of the shaft 2li. The cable winding drums i6@ and itl' are arranged in the chamber on parallel vertical axes alined with the axes of the worm wheels 2 3 and 2|@ respectively. Rotatable with and driven by the worm wheels 2|3 and 2li, respectively, are spur gears 2|5 and 2li; meshing with spur gears 2|? and 2|8, herein arranged on vertical axes spaced equi-distantly from a longitudinal vertical plane including the axis of rotation of the shaft 2| l and parallel with the worm wheel axes. Driven by the spur gears 2H and 258, respectively, are spur gears 2|9 and 220 meshing with spur gears 22| and 222, respectively, herein arranged coaxially with the worm wheels. As in the form of the invention above described, the worm Wheels constitute the high speed terminal driving elements for the cable winding drums, while the spur gears 22| and 222 constitute the low speed terminal driving gears d for the drums, and these gears are connectible in driving relation with the drums by multiple disc clutches in the same manner as that disclosed in Figs. 7 and 8, and the Winding `drums are provided with similar drum release clutches. As a transverse section taken through the axes of the feed drums and the high and low speed terminal driving gears is substantially the same as the transverse section shown in Fig. '7, further description and illustration of this portion of the feeding mechanism is deemed unnecessary other than to state that the cable winding drums may be driven in winding direction at either a high machine haulage speed or a low speed appropriate for cutting, under the control of the disc clutches. In this form of the invention, the retarding frictions or brakes i9, are omitted although it will be evident that such retarding frictions may be readily incorporated in the feed gearing of this form of the invention.

Means is provided for tilting the machine to change the angle in altitude of the kerf cutter, comprising a pair of hydraulic jacks arranged at the opposite sides of the cutter frame section |62. These hydraulic jacks comprise cylinders 225 arranged in a substantially vertical position at the opposite sides of the cutter frame section |62 and rigidly secured to the latter. As shown in Fig. 19, these cylinders contain reciprocable pistons 22% having piston rods 22? extending downwardly through the packed bottom heads 223 of the cylinders. Fixed to the lower ends of the piston rods are shoes 229 engageable with the mine iioor. It is evident that, when fluid pressure is supplied to the upper ends of the cylinders, at

the upper sides of the pistons, the shoes 229 are moved into engagement with the mine ioor and the cutter end of the machine is lifted from the floor, thereby tilting the cutter bar about a transverse axis. When uid pressure is supplied to one or the other of these cylinders, the machine may be tilted about a longitudinal axis, thereby to tilt the cutter bar edgewise. The means for supplying hydraulic pressure to these hydraulic jacks will be later described.

In the illustrative embodiment of the invention shown in Figs. l1 to 20 inclusive, the feeding and cutting mechanisms are essentially the same as those described in the embodiment of the invention described above, with the exception that, in this instance, the motor is arranged intermediate the feeding and cutting mechanisms, and the cutting mechanism is ydriven from one end of the motor and the feeding mechanism from the op-v posite end thereof. This illustrative embodiment of the improved mining machine comprises a cas-- ing |60 of low, compact, generally rectangular shape having a smooth bottom surface ll and adapted to rest upon and slide in any direction over the mine floor. The machine casing iii@ comprises a cutter frame section |82, a motor frame section |63 and a feed frame section |613, the motor frame section |63 arranged intermediate the cutter and feed frame sections, and the casing sections are rigidly united in any suitable manner. Arranged within a transverse horizontal chamber |65 extending across the lower portion of the feed frame section l'i at the end of the machine remote from the cutting mechanism, are relatively rotatable feed operating and controlling members, herein in the form of cable winding drums |66 and ll having respectively wound thereon feeding and controlling cables i558 and |69, while projecting horizontally from the machine casing |50 is an elongated, horizontal, plane lrerf cutter lli).

The driving means for the kerf cutter is shown most clearly in Fig. i3. Arranged in the motor casing section |63 is a motor, herein preferably of the reversible electric type, having its power shaft horizontally disposed and extending longitudinally of the machine with its axis ofv rotation lying in the central longitudinal vertical plane of the machine. Keyed to one end of the motor power shaft is a bevel gear |72 meshing with a bevel gear |73, herein formed integral with a vertical shaft |14. This shaft is suitably journaled within ball bearings supported within the casing section l 52 and has formed integral therewith and driven thereby a spur gear |25 meshing with a. spur gear H6. The spur gear |73 has its hub Vil journaled on ball bearings supported by a vertical shaft H8. This shaft is journaled at its upper end within a ball bearing supported within an upstanding circular bearing support l'lS integral with the casing section |32, while this shaft is journaled near its lower end within a roller bearing supported within a cylindrical bearing support |83 likewise formed integral with the casing section 32. Formed on the hub oi the spur gear V56 are clutch teeth |25 connectible by a sliding clutch member 82 to clutch teeth |33 formed on a clutch member lSfl keyed to the shaft The sliding clutch member |82 is cpeated by a shipper yoke 38 mounted on a transverse shaft |851 rotatably supported within the casing section |32. Fixed to the shaft E83 is a lever |12? pivotally connected to a crank |35 secured to a transverse operating shaft |92 arranged parallel with the shaft 89. Fixed to the .shaft on the exterior of the machine casing is a lever 23; and connected to this lever is an operating cable E94 in the form of a wire rope secured to a flat operating bar H95 guided on and extending longitudinally over the tops of the casing sections |63 and |54 and in turn having secured thereto, at the end of the machine casing remote from the keri cutter, a swiveled operating handle 59E. When the handle E96 is grasped. by ne operator and the cable pulled rearwardly, the shipper yoke is swung to move the clutch member 32 upwardly into its connected position; and', when the handle |36 is released, the clutch member 532 drops downwardly into its disconnected position by gravity. The clutch is held in its connected position. It may be locked therein simply by swinging the handle |96 downwardly into engagement with the end of the machine casing so that the handle abuts the casing. Keyed at the lower end of the vertical shaft |18 and driven thereby is a chain sprocket |55 which engages and drives an endless cutter chain l guided for circulation about the margin of a cutter bar lill of the kerf cutter. It will thus be seen that when the clutch |82 is connected the cutter chain |86 may be driven from the motor power shaft through the bevel gearing |72, H3, spur gears H5, |75 and the vertical shaft |73; and when the clutch is disconnected the cutter chain may remain idle during running of the motor.

The pivotal mounting for the kerf cutter is similar to that of the embodiment of the invention described above, and comprises a hanger frame i9? having a cylindrical bearing portion |93 journaled on a bearing sleeve supported by the cylindrical bearing support |80. Formed integral with the hanger frame is an upstanding frame portion |89 having secured thereto a bearing frame 200 overlying the upper portion of the casing section |52 and journaled on bearing sleeves supported by the circular bearing support |29. The cutter bar lock, for locking the cutter bar in its different angular positions about its pivotal mounting on the machine casing, is essentially the same as that disclosed in Fig. 8, and comprises, as shown in Fig. 18, a vertical cylinder 20| supported within the casing section |62 and containing a plunger 252 secured to a vertically reciprocable locking pin 283. This locking pin is adapted to enter any one of a series of locking apertures 2M formed in the cutter bar hanger frame i9? and is formed with an upper extension 235 guided within a bore oi a guide member 206. Interposed between the upper end of the bore of the guide member and the pin extension is a coil spring 22'! for urging the locking pin toward its locking position. A packing 233 embraces the locking pin to provide a seal between the cylinder bore, at the lower side of the plunger, and the movable locking pin. When pressure fluid is supplied to the cylinder bore at the lower side of the plunger 252, the locking pin is moved upwardly against the tension of the coil spring into its released position.

Now referring to the improved hydraulic control means for the various friction clutches, the drum release clutches, the kerf cutter lock, and the machine tilting jacks, it will be noted that supported on the feed frame section |64 are valve boxes 23| and 232 having horizontal bores containing rotary control valves 233, 234, 235, 23E, 238 and 239, the valves 233, 234 and 235 arranged in the bores of the valve box 23| and the remaining valves arranged in the bores of the valve box 232. The chamber within the feed frame section, within which the feed driving gears are arranged, constitutes an oil reservoir 24|), and formed on the shaft 2|| is an eccentric 24E on which is mounted a ring 242 pivotally connected at 243 to a plunger 244 of a hydraulic pump. This plunger is reciprocable in the bore of a cylinder 245 mounted within the reservoir chamber, and this pump is adapted to draw oil, through an intake valve 246, into the pump cylinder, and to force the oil under pressure from the pump cylinder, past a discharge valve 241 and through suitable conduits, to the various hydraulic cylinders. The discharge side of the pump is connected, through conduits 248 and 24e, to the supply chambers 250 and 25| of the valve boxes 23! and 232. The discharge chambers and 254- of the valve boxes communicate directly with the reservoir chamber. As shown in Fig. 20, the bores of the Valves 233 and 238 are connected, through the conduits 255 and to the operating cylinders for the high speed friction clutches, and through conduits 251 and 253, to the operating cylinders for the slow speed friction clutches. When the valves 233 and 238 are in the position shown in Fig. 20, hydraulic pressure may flow from the supply chambers 25|] and 25|, through passages on the valves and conduits 255 and 256, to the operating cylinders for the high speed clutches to apply the latter, while the operating cylinders for the low speed clutches are connected to the discharge chambers 253 and through the conduits 25l and 258. When the position of the valves 233 and 238 is reversed, hydraulic pressure may be supplied, through conduits 251 and 258, to the operating cylinders for the low speed clutches to apply the latter, while the operating cylinders for the high speed clutches are connected to the discharge chambers through the conduits 255 and 25B. The release clutches for the drums are connected, through conduits 253 and 260, to the bores of the valves 235 and 236, so that, when the valves are in the position shown in Fig. 20, hydraulic pressure may flow from the supply chambers, through passages on the valves and conduits 259 and 269, to the operating cylinders for the drum release clutches to release the latter. When the position of the valves 230 and 236 is reversed,

the operating cylinders for the drum release clutches are connected to discharge chambers through the conduits 255 and 260. The bore for the valve 231 is connected, through conduits 26|, to the release cylinder for the bar locking pin, so that, when the Valve is in the position 

